CN101932814A

CN101932814A - Engine control device and engine control method

Info

Publication number: CN101932814A
Application number: CN2009801038446A
Authority: CN
Inventors: 秋山照夫; 浅田寿士; 大井健
Original assignee: Komatsu Ltd
Current assignee: Komatsu Ltd
Priority date: 2008-02-18
Filing date: 2009-02-18
Publication date: 2010-12-29
Anticipated expiration: 2029-02-18
Also published as: JPWO2009104636A1; US9002590B2; CN102966446A; KR101273988B1; CN102966446B; DE112009000113T5; DE112009000113B4; WO2009104636A1; CN101932814B; KR20100100964A; US20100332102A1; JP5053394B2

Abstract

It is possible to provide an engine control device and an engine control method which can improve engine fuel consumption and smoothly change engine rpm while assuring a pump discharge amount required by a working device. Moreover, it is possible to prevent the uncomfortable feeling of a discontinuous change of the engine rotation sound. A first target engine rpm N1 and a high-speed control region F1 are set in accordance with an instruction value from instruction means. The first target engine rpm N1 is used to set a second target engine rpm N2 of the low-rotation side and a high-speed control region F2. A pump capacity D of a capacity-variable hydraulic pump and an engine torque T are detected. While controlling an engine in the high-speed control region F2, a target engine rpm N corresponding to the detected pump capacity D and the engine torque T are obtained from the relationship between the present pump capacity D and the target engine rpm N and the relationship between the engine torque T and the target engine rpm N. Drive control is performed so that the engine reaches the target engine rpm N.

Description

The control gear of motor and controlling method thereof

Technical field

The present invention relates to carry out the control gear and the controlling method thereof of motor of the drive controlling of motor, particularly relate to the control gear and the controlling method thereof of the motor that the combustion expense of seeking to improve motor consumes based on the target engine speed of the motor of having set.

Background technique

In working truck, if engine load below the rated torque of motor, then carries out in the high speed control zone in the moment of torsion line chart controlling with the coupling of Engine torque.For example, and target setting engine speed corresponding, and definite high speed control zone corresponding with the target engine speed of setting with the setting in the fuel quantity ga(u)ge.

Perhaps, corresponding with the setting in the fuel quantity ga(u)ge and determine the high speed control zone, and the target engine speed of setting motor corresponding with the high speed control zone of determining.So, in the high speed control zone of determining, make the control of engine load and Engine torque coupling.

Usually, in order to improve workload, the majority operation personnel often set target engine speed for the rated speed of motor or near the rotating speed the rated speed.Yet the zone that the fuel consumption of motor is few is that the little zone of oil consumption expense is present in medium rotary speed area or high moment of torsion zone usually on the moment of torsion line chart of motor.Therefore, consider that rotating to the high speed control zone of determining between the specified rotation at zero load fast idle is not the high zone of efficient from the fuel consumption aspect.

In the past, with regard to known such control gear, promptly in order to drive motor in the little zone of fuel consumption, in advance that the target engine speed value of motor is corresponding with the target output torque value of motor and set in each work pattern, thereby can select a plurality of work patterns (for example, with reference to patent documentation 1).In this control gear, when operator for example selected second work pattern, comparing with first work pattern can be with the speed setting of motor in the slow-speed of revolution, thereby can improve fuel consumption.

But, under the situation that adopts aforesaid work pattern switching mode,, just can not improve fuel consumption if operator do not operate again and again to mode switching mechanism.In addition, the engine speed in the time will selecting second work pattern is set under the situation of the tachometer value that is lower than the engine speed when selecting first work pattern without exception, when selecting second work pattern, following problem takes place then.That is, compare during with selection first work pattern, the top speed in the apparatus for work of working truck (hereinafter referred to as Working mechanism) descends.Its result, the workload during with selection first work pattern is compared, and the workload when selecting second work pattern tails off.

Patent documentation 1:(Japan) spy opens flat 10-273919 communique

Summary of the invention

The present invention proposes in order to solve the problem that exists in the above-mentioned prior art, it provides a kind of control gear and controlling method thereof of motor, under the low state of Engine torque, carry out the drive controlling of motor based on second target engine speed of the low speed rotation area side lower than first target engine speed of setting, if when under the high state of Engine torque, using motor, with corresponding and carry out the drive controlling of motor, to reach predefined target engine speed by the pump capacity of engine-driven variable capacity type oil hydraulic pump or detected Engine torque.

A kind of control gear and controlling method thereof of motor particularly are provided, promptly not only can reduce the fuel consumption of motor, guarantee the pump delivery that Working mechanism is required, simultaneously, engine speed is changed very sleekly, and, can prevent that rotation sound by motor from changing discontinuously and the uncomfortable feeling that causes.

Problem of the present invention can be finished by first aspect to the invention of the controlling method of the motor of the invention of the control gear of the motor of fourth aspect record and the record of ten aspects, the 5th aspect to the.

That is, in the control gear of motor of the present invention, have: oil hydraulic pump, it is a variable capacity type, is driven by motor; Hydraulic actuator, it is used to be driven from the pressure oil output of described oil hydraulic pump; Control valve, its control make pressure oil supply with or discharge from described hydraulic actuator to described hydraulic actuator from the pressure oil of described oil hydraulic pump output; Feeler mechanism, it detects the pump capacity and the Engine torque of described oil hydraulic pump; And fuel injection system, the fuel that its control is supplied with to described motor, the topmost of the control gear of this motor is characterised in that to have: command device, it is selected a command value and sends instruction from the command value that can carry out variable instruction; First setting device, its command value of sending according to described command device is set first target engine speed, and based on described first target engine speed of setting, sets second target engine speed lower than described first target engine speed; Second setting device, it sets the pump capacity that detected by described feeler mechanism and the corresponding relation between the target engine speed and the Engine torque that detected by described feeler mechanism and the corresponding relation between the target engine speed; In the drive controlling of the described motor that begins based on described second target engine speed to carry out, corresponding with detected pump capacity of described feeler mechanism or Engine torque and control described fuel injection system, to reach the target engine speed that described second setting device is obtained.

In addition, in the control gear of motor in the present invention, major character is, in the control of the motor that carries out based on described second target engine speed, the control of fuel that the target engine speed based on being obtained by described second setting device in the described fuel injection system is carried out be pump capacity at described oil hydraulic pump greater than the predefined second regulation pump capacity after, perhaps after Engine torque is greater than the predefined second regulation Engine torque, carry out.

In addition, in the control gear of motor in the present invention, major character is, in the control of the motor that carries out based on described first target engine speed, the control of fuel that the target engine speed based on being obtained by described second setting device in the described fuel injection system is carried out be pump capacity at described oil hydraulic pump less than the predefined first regulation pump capacity after, perhaps after Engine torque is less than the predefined first regulation Engine torque, carry out.

In addition, in the control gear of motor in the present invention, major character is, the target engine speed of being obtained by described second setting device is meant, the target engine speed corresponding with described feeler mechanism detected pump capacity and with the corresponding target engine speed of described feeler mechanism detected Engine torque in a high side's target engine speed.

In the controlling method of motor of the present invention, the control gear of this motor has: oil hydraulic pump, and it is a variable capacity type, is driven by motor; Hydraulic actuator, it is used to be driven from the pressure oil output of described oil hydraulic pump; Control valve, its control make pressure oil supply with or discharge from described hydraulic actuator to described hydraulic actuator from the pressure oil of described oil hydraulic pump output; And feeler mechanism, it detects the pump capacity and the Engine torque of described oil hydraulic pump, the topmost of the controlling method of this motor is characterised in that, selects a command value from the command value that can carry out variable instruction, and sets first target engine speed according to the command value of selecting; Set second target engine speed lower based on described first target engine speed of setting than described first target engine speed; Preestablish the corresponding target engine speed of Engine torque that the pump capacity that detects with described feeler mechanism or described feeler mechanism are detected; The drive controlling of the described motor that begins based on described second target engine speed is controlled according to target engine speed in predefined described target engine speed, corresponding with detected pump capacity of described feeler mechanism or Engine torque.

In addition, in the controlling method of motor in the present invention, major character is, in the control of the motor that carries out based on described second target engine speed, the drive controlling of the described motor that carries out based on described target engine speed be pump capacity at described oil hydraulic pump greater than the predefined second regulation pump capacity after, perhaps after Engine torque is greater than the predefined second regulation Engine torque, carry out.

In addition, in the controlling method of motor in the present invention, major character is, in the control of the motor that carries out based on described first target engine speed, the drive controlling of the described motor that carries out based on described target engine speed be pump capacity at described oil hydraulic pump less than the predefined first regulation pump capacity after, perhaps after Engine torque is less than the predefined first regulation Engine torque, carry out.

In addition, in the controlling method of motor in the present invention, major character is, the drive controlling of the described motor that carries out based on described target engine speed is controlled according to the target engine speed corresponding with described feeler mechanism detected pump capacity.

In addition, in the controlling method of motor in the present invention, it is characterized in that the drive controlling of the described motor that carries out based on described target engine speed is controlled according to the target engine speed corresponding with described feeler mechanism detected Engine torque.

In addition, in the controlling method of motor in the present invention, major character is, the drive controlling of the described motor that carries out based on described target engine speed is controlled according to target engine speed in predefined target engine speed, corresponding with described feeler mechanism detected pump capacity with a high side's the target engine speed in the corresponding target engine speed of described feeler mechanism detected Engine torque.

In the control gear and controlling method thereof of motor of the present invention, can set first target engine speed according to the command value that command device sends, and set second target engine speed in the low speed rotation area side based on first target engine speed of setting.Then, if when under the low state of Engine torque, carrying out the drive controlling of motor, can begin the drive controlling of motor based on second target engine speed.Thus, substantially do not change under the situation of working performance of working truck, motor can be transferred to the low zone of fuel consumption and use, thereby can reduce the fuel consumption of motor.

And, can obtain and detected pump capacity or the corresponding target engine speed of detected Engine torque, so, motor can be controlled to reach the target engine speed of obtaining.

By such formation, not only can make engine load and Engine torque coupling, simultaneously, guarantee required pump delivery, and engine speed is changed very sleekly.In addition, owing to can prevent that the rotation sound of motor from changing discontinuously, therefore, can prevent the uncomfortable feeling that the rotation sound by motor brings.And, because engine speed is changed very sleekly, therefore, can reduce fuel consumption significantly.

In addition, in the present invention, when carrying out the drive controlling of motor with second target engine speed, before the pump capacity of variable capacity type oil hydraulic pump reaches more than the predefined second regulation pump capacity, before perhaps Engine torque reaches more than the predefined second regulation Engine torque, carry out the drive controlling of motor with second target engine speed.So more than reaching the second regulation pump capacity or after more than the second regulation Engine torque, the drive controlling of carrying out motor is to reach and detected pump capacity or the corresponding target engine speed of detected Engine torque.

Thus, can be under the optimum state of the operating conditions that is suitable for Working mechanism that operator pursued, engine revolution is driven,, can access the maximum of rotating the motor that drives in the best condition and export and pressure oil output as the variable capacity type oil hydraulic pump.Therefore, in the big digging operation of load etc., in the operation of the maximum output that needs motor, can bring into play and former identical working performance.

And, in the present invention, when carrying out the drive controlling of motor with first target engine speed, during before pump capacity in the variable capacity type oil hydraulic pump reaches below the predefined first regulation pump capacity, before perhaps Engine torque reaches below the predefined first regulation Engine torque, carry out the drive controlling of motor with first target engine speed.Then, more than reaching the first regulation pump capacity or after more than the first regulation Engine torque, the drive controlling of carrying out motor is to reach and detected pump capacity or the corresponding target engine speed of detected Engine torque.

Thus, when carrying out the drive controlling of motor with first target engine speed, during before pump capacity in the variable capacity type oil hydraulic pump reaches below the predefined first regulation pump capacity, before perhaps Engine torque reaches below the predefined first regulation Engine torque, can guarantee the high-engine moment of torsion.So, below the pump capacity in the variable capacity type oil hydraulic pump reaches the predefined first regulation pump capacity, it is following and when not needing the high-engine moment of torsion that perhaps Engine torque reaches the predefined first regulation Engine torque, corresponding with detected pump capacity or Engine torque, make engine speed be set in the low low target engine speed of first target engine speed of specific fuel consumption.Owing to can carry out the drive controlling of motor like this, therefore, can reduce the fuel consumption of motor.

In addition, in the present invention, target engine speed during as the drive controlling of carrying out motor, can use with the corresponding target engine speed of detected pump capacity and with the corresponding target engine speed of detected Engine torque in the target engine speed of higher side.

By such formation, on the moment of torsion line chart, can pass through the exportable maximum rated power point of motor, under the state of guaranteeing the pump delivery that hydraulic actuator is required, can carry out the drive controlling of motor sleekly with the high state of efficient.

In the present invention, when not needing high Engine torque, can carry out the drive controlling of motor with the low target engine speed of fuel consumption, thereby can reduce the fuel consumption of motor, simultaneously, guarantee required pump delivery.And, though be aforesaid simple structure,, can make the variable capacity type oil hydraulic pump obtain the maximum output of motor, and can reduce the fuel consumption of motor.

In addition, can utilize the value at the swash plate angle of detecting oil hydraulic pump or the relation of expression pump capacity, obtain the pump capacity that will detect.Relation as the expression pump capacity, adopt the output of for example representing the variable capacity type oil hydraulic pump to press the T=PD/200 π of the relation between P and output capacity D (pump capacity D) and the Engine torque T, can obtain the pump capacity of the oil hydraulic pump of this moment from the D=200 π T/P of this derivation of equation.

In addition, for the pressure reduction of in the apparatus for controlling pump at the swash plate angle of controlling the variable capacity type oil hydraulic pump, setting (being commonly referred to load sensing pressure reduction), the relation of the pressure reduction of pressing with the load of hydraulic actuator etc. is pressed in the pump output of employing variable capacity type oil hydraulic pump, can obtain pump capacity.

And the Engine torque that can use known detections such as Engine torque detector to detect also can adopt from the output of pump capacity and pump and press suitable methods such as obtaining Engine torque to obtain the Engine torque that will detect.

In the present invention, can based between first target engine speed, second target engine speed and first target engine speed and second target engine speed with detected pump capacity or the corresponding target engine speed of detected Engine torque, in the T-N of motor line chart (the moment of torsion line chart that constitutes by Engine torque axle and engine speed axle), set corresponding respectively high speed control zone.

In addition, carry out the drive controlling of motor by using the target engine speed corresponding with detected pump capacity, corresponding with pump capacity in the variable capacity type oil hydraulic pump of current time, can determine the target engine speed of following successively.

Like this, by determining target engine speed successively, can be controlled to be the pump capacity that makes in the variable capacity type oil hydraulic pump and reach best pump capacity.Therefore, even the pump capacity change in the variable capacity type oil hydraulic pump also can be followed the pump capacity of the oil hydraulic pump of target engine speed change, can guarantee the output flow that hydraulic actuator is required at short notice.

In addition, by using the drive controlling of carrying out motor corresponding to the target engine speed of detected Engine torque, also can access with the testing pump capacity and obtain target engine speed and carry out the identical effect of situation of the drive controlling of motor.

And, when use is carried out the drive controlling of motor corresponding to the target engine speed of detected Engine torque, on the moment of torsion line chart, can pass through the exportable maximum rated power point of motor.In addition, when use is carried out the drive controlling of motor corresponding to the target engine speed of detected pump capacity, if do not reach first target engine speed, though then can pass through maximum power point on the moment of torsion line chart, this maximum power point is less than the maximum rated power point.

Like this, can carry out control in each high speed control zone.And, in the present invention, the control in these high speed control zones also is included in according to the engine control of carrying out with the corresponding target engine speed of detected pump capacity or detected Engine torque between first target engine speed, second target engine speed and first target engine speed and second target engine speed.

Description of drawings

Fig. 1 is the hydraulic circuit diagram of embodiment of the present invention; (embodiment)

Fig. 2 is the moment of torsion line chart of motor; (embodiment)

Fig. 3 is the moment of torsion line chart when increasing Engine torque; (embodiment)

Fig. 4 is the moment of torsion line chart when reducing Engine torque; (embodiment)

Fig. 5 is a control flow chart of the present invention; (embodiment)

Fig. 6 is the skeleton diagram of control gear; (embodiment)

Fig. 7 is the figure that concerns between expression pump capacity and the target engine speed; (embodiment)

Fig. 8 is the figure that concerns between expression engine speed and the Engine torque; (illustrative examples)

Fig. 9 is the figure that concerns between expression engine speed and the Engine torque; (embodiment)

Figure 10 is the figure that concerns between Engine torque and the target engine speed; (embodiment)

Figure 11 is the hydraulic circuit diagram of neutral fully opened type; (embodiment)

Figure 12 is the minus flow control type hydraulic circuit diagram in the neutral fully opened type oil hydraulic circuit; (embodiment)

Figure 13 is the figure of control characteristic of the minus flow control type oil hydraulic circuit of expression Figure 12; (embodiment)

Figure 14 is the figure of pump control characteristic of the minus flow control type oil hydraulic circuit of expression Figure 12; (embodiment)

Figure 15 is the positive flow control type hydraulic circuit diagram in the neutral fully opened type oil hydraulic circuit; (embodiment)

Figure 16 is the figure of pump control characteristic of the positive flow control type oil hydraulic circuit of expression Figure 15.(embodiment)

Description of reference numerals

2 motors

3 fuel injection systems

4 fuel quantity ga(u)ges (command device)

6 variable capacity type oil hydraulic pumps

7 controllers

8 apparatus for controlling pump

9 control valves

11 function lever apparatus

12 servocylinders

17 LS valves

32 fuel quantity ga(u)ge command value operational parts

32a first setting device

32b second setting device

50 variable capacity type oil hydraulic pumps

53 the 3rd control valves

54 centre by-pass loops

55 throttle valve

57 servo-hydraulic actuators

58 servo pilot valves

59 minus flow control valves

71 first pilot valves

72 second pilot valves

73 the 3rd pilot valves

75 controllers

76 apparatus for controlling pump

F1～F4 high speed control zone

Fa～Fc high speed control zone

A first desired location

B second desired location

The Nh rated speed

K1 maximum rated power point

R Maximum Torque line

Fuel consumption curves such as M

Embodiment

Below, specify preferred implementation of the present invention with reference to accompanying drawing.The control gear of motor of the present invention and the controlling method of motor are installed in the control gear and the controlling method of diesel engine of working trucks such as hydraulic shovel, bulldozer, wheel loader as control very suitable.

Controlling method as the control gear and the motor of motor of the present invention except the shape and structure of following explanation, so long as can solve the shape and the structure of problem of the present invention, also can adopt shape and structure except that following explanation.Therefore, the present invention is not limited to the embodiment of following explanation, can carry out various changes to present embodiment.

Embodiment

Fig. 1 is the oil hydraulic circuit in the controlling method of the control gear of motor of embodiment of the present invention and motor.Motor 2 is diesel engine, and the control of this Engine torque is to be undertaken by adjust the fuel quantity that sprays in the cylinder body of motor 2.The adjustment of this fuel quantity can utilize known fuel injection system 3 to carry out.

Be connected with variable capacity type oil hydraulic pump 6 (hereinafter referred to as oil hydraulic pump 6) on the output shaft 5 of motor 2, the rotation by output shaft 5 drives oil hydraulic pump 6.The inclination angle of the swash plate 6a of oil hydraulic pump 6 is controlled by apparatus for controlling pump 8, by changing the inclination angle of swash plate 6a, changes the pump capacity D (cc/rev) of oil hydraulic pump 6.

Apparatus for controlling pump 8 is made of the servocylinder 12 and the LS valve (load-sensing valve) 17 at the inclination angle of control swash plate 6a, and wherein, the pressure reduction that the LS valve is pressed according to the load of pump pressure and hydraulic actuator 10 is controlled.Servocylinder 12 has the servopiston 14 that acts on swash plate 6a, from the output pressure energy of oil hydraulic pump 6 enough by

oil circuit

27a, 27b output.LS valve 17 presses the pressure reduction of pressing with the load of the hydraulic actuator of being exported by guide's oil circuit 28 10 to move according to the output of being exported by oil circuit 27a, and servopiston 14 is controlled in the action of LS valve 17.

The inclination angle of swash plate 6a in the oil hydraulic pump 6 is controlled by control servopiston 14.In addition, by controlling control valve 9 according to the operation amount of operating stem 11a, the flow that control is supplied with to hydraulic actuator 10.This apparatus for controlling pump 8 can be made of known load sensing controlled device.

Pressure oil by oil hydraulic pump 6 outputs supplies to control valve 9 through output circuit 25.Control valve 9 constitutes the switching valve that can switch to three-position five-way, can pass through to

oil circuit

26a, and 26b selects to supply with the pressure oil by control valve 9 outputs, makes hydraulic actuator 10 actions.

As hydraulic actuator, can not be interpreted as being only limited to illustrative cylinder type hydraulic actuator, can be oil hydraulic motor, in addition, also can constitute rotary-type hydraulic actuator.Though only illustration the combination of one group of control valve 9 with hydraulic actuator 10,, can constitute the combinations of many group control valves 9 and hydraulic actuator 10, can also constitute by a control valve and operate a plurality of hydraulic actuators.

Promptly, for example be example explanation hydraulic actuator, then go for big arm and sail with oil hydraulic motor, right travel oil hydraulic motor, revolution motor etc. with oil hydraulic cylinder, left lateral with oil hydraulic cylinder, scraper bowl with oil hydraulic cylinder, forearm as hydraulic actuator as working truck if with the hydraulic shovel.In these hydraulic actuators, for example big arm is illustrated among Fig. 1 as representative with oil hydraulic cylinder.

When from neutral position operation operating stem 11a, according to direction of operating and the operation amount of operating stem 11a, from function lever apparatus 11 output pilot pressures.The pilot pressure of output is applied in the left and right sides pilot port of control valve 9 any.Thus, control valve 9 is switched to (I) position in left side or (III) position on right side from (II) position of neutral position.

When control valve 9 when (II) position is switched to (I) position, then can supply with pressure oil output to the bottom side of hydraulic actuator 10 from oil circuit 26b from oil hydraulic pump 6, can make the piston elongation of hydraulic actuator 10.At this moment, the pressure oil of the head side of hydraulic actuator 10 is discharged to fuel tank 22 through control valve 9 from oil circuit 26a.

Similarly, when control valve 9 is switched to (III) position, then can supply with pressure oil output to the head side of hydraulic actuator 10, the piston of hydraulic actuator 10 is shortened from oil circuit 26a from oil hydraulic pump 6.At this moment, the pressure oil of the bottom side of hydraulic actuator 10 is discharged to fuel tank 22 through control valve 9 from oil circuit 26b.

From the branch midway of output circuit 25 oil circuit 27c is arranged, in oil circuit 27c, be provided with unloading valve 15.Unloading valve 15 is connected with fuel tank 22, and can be switched to the position of blocking-up oil circuit 27c and connection oil circuit 27c.Hydraulic pressure among the oil circuit 27c is as unloading valve 15 being switched to the extruding force effect that is communicated with the position.

In addition, the pilot pressure of guide's oil circuit 28 that the load of released liquor pressure actuator 10 is pressed and the spring force that applies the spring of certain pressure reduction are as the extruding force effect that unloading valve 15 is switched to blocking position.Unloading valve 15 is controlled according to the pilot pressure of guide's oil circuit 28 and the spring force of spring and the pressure reduction of the hydraulic pressure among the oil circuit 27c.

When operator operation is selected a command value as the fuel quantity ga(u)ge 4 of command device from the command value that can carry out variable instruction, then can set the target engine speed corresponding with the command value of selecting.According to first target engine speed of such setting, can set the high speed control zone that makes engine load and Engine torque coupling.

That is, as shown in Figure 2,, then select high speed control zone Fb corresponding to target engine speed Nb (N ' b) if operating and setting first target engine speed of based on fuel table 4 is target engine speed Nb (N ' b).At this moment, the target engine speed of motor becomes rotational speed N b (N ' b).

Target engine speed N ' the b of motor is determined as the match point of the aggregate value of the loss moment of torsion of the friction torque of motor when the target engine speed with motor is controlled to be rotational speed N b, under the zero load situation and hydraulic system and Engine torque.In the engine control of reality, the line of linking objective engine speed N ' b and match point Ps is set at high speed control zone Fb.

At this, if operating fuel quantity ga(u)ge 4, operator set the low target engine speed Nc of the first target engine speed Nb that is different from initial selection (N ' b) (N ' c), then the high speed control of low speed rotation area side zone Fc is set to the high speed control zone.The target engine speed Nc that sets this moment (N ' c) becomes second target engine speed.

Like this, by setting fuel quantity ga(u)ge 4, can set one with can be by the corresponding high speed control zone of target engine speed of fuel quantity ga(u)ge 4 selections.Promptly, by selecting fuel quantity ga(u)ge 4, for example shown in Figure 2, can set a plurality of high speed control zone Fb that is positioned at the low speed rotation area side by the regional Fa of the high speed control of maximum rated power point K1, with respect to this high speed control zone Fa, Fc, ... in any high speed control zone, perhaps be positioned at any high speed control zone of the centre in these high speed control zones.

The performance that in the moment of torsion line chart of Fig. 3, can export by the region representation motor 2 of Maximum Torque line R regulation.Maximum rated power point K1 on Maximum Torque line R (hereinafter referred to as maximum rated power point K1), it is maximum that the output of motor 2 (power) becomes.M represents the fuel consumption curve that waits of motor 2, and the central side that waits fuel consumption curve is the fuel consumption Minimum Area.

Below, illustrating the maximum target engine speed of setting the motor corresponding with the command value of fuel quantity ga(u)ge 4 is target engine speed N1 (N ' 1), and the situation of the setting high speed control of the passing through maximum rated power point K1 regional F1 corresponding with target engine speed N1 (N ' 1).That is, situation as the first target engine speed target setting engine speed N1 (N ' 1) is described.At this moment, main with reference to Fig. 1, Fig. 3 and Fig. 4 and use the control flow chart of Fig. 5 and the system block diagram of Fig. 6, when illustrate engine load with the Engine torque coupling on the regional F1 of high speed control mobile control flow.

Though below explanation set the maximum target engine speed N1 as engine speed (N ' 1) corresponding, and set the situation of the corresponding therewith regional F1 of the high speed control of passing through maximum rated power point K1 as first target engine speed with the command value of fuel quantity ga(u)ge 4, but the present invention is not limited to situation about being set with by the high speed control zone F1 of maximum rated power point K1.For example, even according to the first target engine speed N1 that sets, set a plurality of high speed control zone Fb among Fig. 2, Fc, ... in any high speed control zone, perhaps be positioned at a plurality of high speed control zone Fb, Fc, ... any high speed control zone of centre, the present invention also can be applicable to each high speed control zone of setting well.

Situation when Fig. 3 represents that Engine torque increases gradually, the situation when Fig. 4 represents that Engine torque reduces gradually.Fig. 7 is the figure that is used to illustrate the corresponding relation between detected pump capacity D and the target engine speed.Fig. 8 to Figure 10 is the figure that is used to illustrate the corresponding relation between detected Engine torque and the target engine speed.Fig. 8 is the figure of the presuming method of expression Engine torque, and Fig. 9 is the moment of torsion line chart that detected Engine torque is used in expression, and Figure 10 is the figure that is used to illustrate the corresponding relation between detected Engine torque and the target engine speed.

In addition, Fig. 5 represents control flow.The part of surrounding with dot and dash line in Fig. 6 is represented controller 7.Relation in Fig. 5 and Fig. 7 between expression pump capacity D and the target engine speed N, the relation in Fig. 5 and Figure 10 between expression detection torque T and the target engine speed N is an illustration in the relation of this expression, also can set other relation curves etc.

At first, use Fig. 6 that the control of controller 7 is described.In Fig. 6, in the fuel quantity ga(u)ge command value operational part 32 in controller 7, not only import the command value 37 of fuel quantity ga(u)ge 4, also import the pump capacity and the detected Engine torque of detected oil hydraulic pump 6.In fuel quantity ga(u)ge command value operational part 32, be provided with the first setting device 32a and the second setting device 32b.About the first setting device 32a and the second setting device 32b, will narrate in the back.

From the target engine speed of fuel quantity ga(u)ge command value operational part 32 output motors 2, set fresh fuel table command value 35.Then, the fresh fuel table command value of setting 35 is sent to the fuel injection system 3 (with reference to Fig. 1) of motor 2 and carry out the drive controlling of motor 2.

As the detected pump capacity of the oil hydraulic pump 6 that is input to fuel quantity ga(u)ge command value operational part 32, can directly use testing signal from pump capacity sensor 39, perhaps can use the pump capacity of computing in pump capacity operational part 33.

In pump capacity operational part 33, input has by the detected pumps output of pump pressure sensor 38 presses and engine torque command value 41 or from the output signal of Engine torque operational part II (42).Generally, the output of the pump of oil hydraulic pump 6 presses the relation of P, output capacity D (pump capacity D) and Engine torque T (Engine torque T) to be represented by formula T=PD/200 π.From the formula D=200 π T/P that this relation is derived, can obtain the pump capacity D of certain oil hydraulic pump 6 constantly.

In addition, pump pressure sensor 38 can be arranged to for example can to detect pumping pressure in the output circuit 25 of Fig. 1.In addition, pump capacity sensor 39 can constitute the sensor at the swash plate angle of detecting oil hydraulic pump 6 etc.

Engine torque command value 41 is to be the engine torque command value that purpose is possessed in control gear inside with the engine control.In pump capacity operational part 33, press the Engine torque value of removing engine torque command value 41 or exporting by using by Engine torque operational part II (42) by pump pressure sensor 38 detected pump outputs, obtain pump capacity.

In pump capacity operational part II (42), input has by engine rotation speed sensor 20 detected engine speed and fresh fuel table command value 35.In pump capacity operational part II (42), can use as shown in Figure 8 Engine torque T and the graph of a relation between the engine speed N etc., and use the value that is input to pump capacity operational part II (42), computing Engine torque.

Promptly, as shown in Figure 8, on the Fn of high speed control zone, can be from this high speed control zone Fn and intersection point by engine rotation speed sensor 20 detected certain engine speed Nr constantly, that obtains certain motor constantly infers torque T g, wherein, high speed control zone Fn is by being that target engine speed Nn is corresponding and by 35 settings of fresh fuel table command value with certain target engine speed Nn constantly.

In addition, in Engine torque operational part II (42), can be worth 41 and calculate certain Engine torque constantly from engine torque command by engine rotation speed sensor 20 detected engine speed.

As the detected Engine torque that is input to fuel quantity ga(u)ge command value operational part 32, can use torque value by Engine torque operational part I (40) or Engine torque operational part II (42) output.

In Engine torque operational part II (42), carry out aforesaid computing and obtain Engine torque.In addition, in Engine torque operational part I (40), can be from pressing by pump capacity sensor 39 detected pump capacities with by the detected pumps output of pump pressure sensor 38, the output torque of computing oil hydraulic pump 6, the moment of torsion that this computing is arrived is as certain Engine torque constantly.

In Fig. 6, the input signal of pump capacity operational part 33, engine torque command value 41 and Engine torque operational part II (42) and output signal with dashed lines are respectively represented.Why with dashed lines is represented, is because in order to represent that these operational parts, command value can use as the replacing method of obtaining pump capacity, Engine torque.

Then, the control flow of explanatory drawing 5.

In the step 1 of Fig. 5, controller 7 reads the command value of fuel quantity ga(u)ge 4.Read the command value of fuel quantity ga(u)ge 4 when controller 7 after, then be transferred to step 2.

In step 2, controller 7 is set the first target engine speed N1 (N ' 1) according to the command value of the fuel quantity ga(u)ge 4 that reads, and according to the first target engine speed N1 (N ' 1) the setting high-speed control area F1 that sets.

Although understand the main points of setting the first target engine speed N1 (N ' h) of motor 2 according to the command value of the fuel quantity ga(u)ge 4 that reads at first, but, also setting high-speed control area F1 at first, and set the first target engine speed N1 (N ' 1) according to the high speed control zone F1 that sets.Perhaps, also can set first target engine speed N1 (N ' 1) and high speed control zone F 1 simultaneously according to the command value of the fuel quantity ga(u)ge 4 that reads.

As shown in Figure 3, after setting first target engine speed N1 (N ' 1) and high speed control zone F1, then be transferred to step 3.

In Fig. 3, the fast idle point N ' 1 that connects maximum target engine speed N1 is represented as high speed control zone F1 with the line of maximum rated power point K1.This fast idle point N ' 1 has been as having mentioned in the explanation of the high speed control zone Fb that uses Fig. 2, can be used as the aggregate value of loss moment of torsion of target engine speed with motor engine friction torque when being controlled to be maximum target engine speed Nh, under the zero load situation and hydraulic system and Engine torque coupling point and be determined.

In step 3, controller 7 utilizes the first setting device 32a to determine the corresponding and predefined second target engine speed N2 (N ' 2) of low speed rotation area side, the high speed control zone F2 corresponding with target engine speed N2 (N ' 2) of being positioned at the first target engine speed N1 (N ' 1), high speed control zone F1.

As high speed control zone F2, compare with situation about for example when operating the operating stem 11a of hydraulic shovel, controlling, because of load sensing controlled is set as the high speed control zone that service speed can descend hardly at high speed control zone F1.

That is, the target engine speed N2 corresponding to high speed control zone F2 can be set for: for example reduce 10% than target engine speed Nh corresponding to high speed control zone F1.Here for example understand target engine speed set for and reduce by 10% situation, but this numerical value is illustration, and do not mean that and limit the invention to this numerical value.

Like this, corresponding with each high speed control zone F1 that can in fuel quantity ga(u)ge 4, set, can will more set as the high speed control zone corresponding than this high speed control zone F1 in advance with each high speed control zone F1 by the high speed control zone F2 of low speed rotation area side.

High speed control zone F2 is determined by controller 7, and is transferred to step 4.

In step 4, when operating operation bar 11a, then shown in the thin dotted line of Fig. 3, controller 7 carries out the control of fuel injection system 3, so that the coupling of engine load and Engine torque is carried out on the F2 of high speed control zone.

When operator's operating operation bar 11a begins to increase the control of Working mechanism speed of hydraulic shovel, then carry out from the control of step 5 or from the control of step 8.As narrating in the back, under utilizing, then carry out from the control of step 5 and from the control of step 8 corresponding to the target engine speed N of detected pump capacity D and situation corresponding to the target engine speed N target engine speed of detected Engine torque T.

Step 5 to the control conduct of step 7 is obtained corresponding to the control step of the target engine speed N of the pump capacity D of detected oil hydraulic pump 6 and is constituted, and step 8 to the control conduct of step 11 is obtained corresponding to the control step of the target engine speed N of detected Engine torque T and constituted.Step 5 to the control and step 8 to the control of step 11 of step 7 is undertaken by the second setting device 32b.

At first, illustrate and obtain the control step corresponding to the target engine speed of detected pump capacity of step 5 to the step 7.

In step 5, read pump capacity D by pump capacity sensor 39 detected oil hydraulic pumps 6.In step 5, after reading pump capacity D, then be transferred to step 6.Pump capacity D can press relation between P, output capacity D (pump capacity D) and the Engine torque T (Engine torque T) etc. to obtain from the output of aforesaid pump.

In step 6, obtain corresponding to the control of the target engine speed N of detected pump capacity D roughly as follows.That is, as shown in Figure 7, when carrying out the drive controlling of motor, before the pump capacity D of oil hydraulic pump 6 reaches the second regulation pump capacity D2, control based on the second target engine speed N2 based on the second target engine speed N2.

When the pump capacity D of detected oil hydraulic pump 6 reaches the second regulation pump capacity D2 when above, based on as shown in Figure 7 predefined pump capacity D and the corresponding relation between the target engine speed N, obtain target engine speed N corresponding to detected pump capacity D.At this moment, carry out the drive controlling of motor 2 to reach the target engine speed Nn that obtains.

Then, during before target engine speed Nn reaches the first target engine speed N1 or the second target engine speed N2, all the time obtain target engine speed Nn, and control the driving of motor 2 with the target engine speed Nn that obtains all the time corresponding to detected pump capacity Dn.

For example, when the detected pump capacity D of current time was pump capacity Dn, target engine speed N can be used as target engine speed Nn and obtains.Then, as long as detect state, then obtain target engine speed Nn+1 again corresponding to pump capacity Dn+1 from Fig. 7 from the change of state of pump capacity Dn to pump capacity Dn+1.Then, carry out the drive controlling of motor 2 to reach the target engine speed Nn+1 that obtains again.

When detected pump capacity D reaches the first regulation pump capacity D1, carry out the drive controlling of motor 2 based on the first target engine speed N1.Then, when carrying out the drive controlling of motor 2, before the pump capacity D of oil hydraulic pump 6 reaches below the first regulation pump capacity D1, proceed the drive controlling of motor 2 based on the first target engine speed N1 based on the first target engine speed N1.

In addition, under the state between the first regulation pump capacity D1 and the second regulation pump capacity D2, under the situation before the Maximum Torque line R that reaches as shown in Figure 3, R carries out the control of motor along the Maximum Torque line at detected pump capacity D.

Get back to Fig. 5 and go on to say control step 6.In step 6, behind the target engine speed N that obtains based on the corresponding relation between predefined pump capacity D and the target engine speed N corresponding to detected pump capacity D, then be transferred to step 7.

In step 7, according to variance ratio, the variance ratio of pump delivery pressure or the variance ratio revise goal engine speed N value of Engine torque T of the pump capacity of oil hydraulic pump 6.Just, when the degree that promptly increases when these variance ratio is high, can be with target engine speed toward a high side correction.

Though in step 7, put down in writing the control step of revise goal engine speed N value, also can constitute the control of skips steps 7.

Then description of step 8 is obtained the control step corresponding to the target engine speed of detected Engine torque in the step 11.

In step 8 in step 11, based on according to describing among Fig. 6 from the testing signal of pump capacity sensor 39 with from the testing signal of pump pressure sensor 38 structure from Engine torque operational part I (40) output Engine torque T.But,, can use Engine torque operational part II formations such as (42) as the such structure of detection of engine torque T as mentioned above.Structure about from Engine torque operational part I (40) or Engine torque operational part II (42) computing Engine torque T can replace with the explanation of above-mentioned relevant Engine torque operational part I (40) and Engine torque operational part II (42).

In step 8, behind the testing signal and testing signal that read from pump capacity sensor 39, then change step 9 over to from pump pressure sensor 38.

In step 9,, calculate Engine torque T based on the testing signal that in step 8, reads.After calculating Engine torque T, then change step 10 over to.

Obtaining corresponding to the control of the target engine speed N of detected Engine torque T in step 10 is roughly as follows.That is, as shown in figure 10, when carrying out the drive controlling of motor, before detected Engine torque T reaches the second regulation Engine torque T2, control based on the second target engine speed N2 based on the second target engine speed N2.

When detected Engine torque T reaches the second regulation Engine torque T2 when above, based on as shown in figure 10 predefined Engine torque T and the corresponding relation between the target engine speed N, obtain target engine speed N corresponding to detected Engine torque T.At this moment, carry out the drive controlling of motor 2 to reach the target engine speed N that obtains.

Then, during before target engine speed N reaches the first target engine speed N1 or the second target engine speed N2, all the time obtain target engine speed N, and carry out the drive controlling of motor 2 according to the target engine speed N that obtains corresponding to detected Engine torque T.

For example, when the detected Engine torque T of current time was Engine torque Tn, target engine speed N can be used as target engine speed Nn and obtains.Then, when detecting the state of Engine torque T, then obtain target engine speed Nn+1 again corresponding to Engine torque Tn+1 from Figure 10 from the change of state of Engine torque Tn to Engine torque Tn+1.Then, carry out the drive controlling of motor 2 to reach the target engine speed Nn+1 that obtains again.

When detected Engine torque T reaches the first regulation Engine torque T1, carry out the drive controlling of motor 2 based on the first target engine speed N1.Then, when carrying out the drive controlling of motor 2 based on the first target engine speed N1, before detected Engine torque T reaches below the first regulation Engine torque T1, proceed the drive controlling of motor 2 based on the first target engine speed N1.

In addition, by obtaining corresponding to the target engine speed N of detected Engine torque T and carrying out the drive controlling of motor 2, as shown in Figure 9, on the moment of torsion line chart of motor, can pass through motor 2 exportable maximum rated power points.

Getting back to Figure 10 proceeds to be described as follows.When detected Engine torque T is between the first regulation Engine torque T1 and the second regulation Engine torque T2, when detected Engine torque Tn+1 change next time, then obtain the target engine speed Nn+1 of the new Engine torque Tn+1 correspondence of change.Then, based on this target engine speed Nn+1 that obtains again, carry out the drive controlling of motor 2 successively.

Get back to Fig. 5 and go on to say control step 10.In step 10, the target engine speed N when obtaining based on the corresponding relation between predefined Engine torque T and the target engine speed N corresponding to detected Engine torque T then changes step 11 over to.

In step 11, according to variance ratio, the variance ratio of pump delivery pressure or the variance ratio of Engine torque T of the pump capacity of oil hydraulic pump 6, revise goal engine speed N value.Just, when the degree that promptly increases when these variance ratio is high, with target engine speed N toward a high side correction.

Though in step 11, put down in writing the control step of revise goal engine speed N value,, also can constitute the control of skips steps 11.

When step 5 being controlled at corresponding to the target engine speed N of detected pump capacity D and when using the high side's of rotating speed target engine speed in corresponding to the target engine speed N of detected Engine torque T, carrying out the control of step 5 to the control of step 7 and step 8 to step 11 to the control of step 7 and step 8 to step 11.At this moment, then step 7 and step 11 are carried out the control of step 12.

When utilizing target engine speed N corresponding to detected pump capacity D to carry out the drive controlling of motor 2, perhaps when utilizing target engine speed N corresponding to detected Engine torque T to carry out the drive controlling of motor 2, the control of skips steps 12 and change step 13 over to.

In step 12, in the target engine speed of selecting the high side of rotating speed corresponding to the target engine speed N of detected pump capacity D and in corresponding to the target engine speed N of detected Engine torque T.After the target engine speed of selecting the high side of rotating speed, then change step 13 over to.

In step 13, owing to carry out the drive controlling of motor with target engine speed N, so export fresh fuel table command value 35 shown in Figure 6.In step 14, read in the fresh fuel table command value 35 of being instructed in the step 13.

In step 15, judge whether the fresh fuel table command value of re-entering 35 is different from the fresh fuel table command value 35 of input before.

In step 15, when be judged as the fresh fuel table command value of re-entering 35 be different from before the input fresh fuel table command value 35 time, get back to step 2, carry out the later control of step 2 repeatedly.In addition, in step 15, when the fresh fuel table command value 35 that is judged as the fresh fuel table command value 35 re-entered and input before is identical, promptly when being judged as fresh fuel table command value 35 by change, get back to step 5 or step 8, carry out the later control of step 5 or step 8 repeatedly.

Control when then, utilizing Fig. 1 to summarize operation.That is testing pump capacity D and the control carried out describes when operating operation bar 11a increases the Working mechanism speed of hydraulic shovel significantly operator.The explanation of having controlled though omitted the detection of engine torque T,, carry out the identical control of control with testing pump capacity D.

When making control valve 9 for example be switched to (I) position as the operating stem 11a in the application drawing 1 significantly, control valve 9 increases at the opening area 9a of (I) position, the pump output in the oil circuit 25 press with guide's oil circuit 28 in the load pressure reduction of pressing descend.At this moment, the apparatus for controlling pump 8 that constitutes as the load sensing controlled device moves towards the direction of the pump capacity D that increases oil hydraulic pump 6.

In addition, can set the second regulation pump capacity D2, also can set the second regulation pump capacity D2 with the following pump capacity of maximum pump capacity with the maximum pump capacity value in the oil hydraulic pump 6.Illustrate the situation of setting the regulation pump capacity as the second regulation pump capacity D2 below.When the pump capacity of oil hydraulic pump 6 when the state of the second regulation pump capacity D2 increases, carry out target engine speed N is transformed into control corresponding to the target engine speed N of detected pump capacity D shown in Figure 7 from the second target engine speed N2.

The state that the pump capacity of oil hydraulic pump 6 reaches the second regulation pump capacity D2 can utilize the following various parameter values that will illustrate to detect.As the feeler mechanism of pump capacity, can constitute the feeler mechanism that to detect at the various parameter values of following explanation.

Parameter value as the pump capacity D that can detect oil hydraulic pump 6, under the situation of the value of using Engine torque T, controller 7 can be specific for the position on the high speed control zone F2 of this engine speed from the engine speed that is detected by engine rotation speed sensor 20 based on the moment of torsion line chart that is stored in controller 7.Based on certain location, can obtain the Engine torque value of this moment.Like this, by the Engine torque value is used as parameter value, can detect that the output quantity from oil hydraulic pump 6 reaches from the state of oil hydraulic pump 6 exportable maximum outputs in the F2 of high speed control zone.

Under the situation that the pump capacity with oil hydraulic pump 6 uses as parameter value, the output of oil hydraulic pump 6 presses the available formula T=PD/200 of the relation π between P, output capacity D (pump capacity D) and the Engine torque T to represent.Can obtain the pump capacity of the oil hydraulic pump 6 of this moment from the formula D=200 π T/P that utilizes this relation to derive.As Engine torque T, for example can use the command value of the Engine torque that remains on controller inside.

Perhaps, can swash plate angle transducer (not shown) be installed on oil hydraulic pump 6 and directly measure the pump capacity of oil hydraulic pump 6, thereby obtain the pump capacity of oil hydraulic pump 6.Utilize the pump capacity of the oil hydraulic pump of obtaining like this 6, the pump capacity that can detect oil hydraulic pump 6 in the F2 of high speed control zone reaches the state of the second regulation pump capacity D2.

The pump capacity of oil hydraulic pump 6 reaches the state of the second regulation pump capacity D2 among the comfortable high speed control zone F2, when operator in order to improve Working mechanism speed further significantly during operating operation bar 11a, carry out the drive controlling of motor 2, to reach target engine speed N corresponding to detected pump capacity D shown in Figure 7.At this moment, transfer to the control in best high speed control zone the regional F1 successively to high speed control from high speed control zone F2.

After transferring to high speed control zone F 1, when the load of hydraulic actuator 10 further increased, Engine torque rose.In the F1 of high speed control zone, under the further situation about increasing of the load of hydraulic actuator 10, the pump capacity D of oil hydraulic pump 6 increases to maximum pump capacity, and Engine torque rises to maximum rated power point K1.In addition, between high speed control zone F1 and high speed control zone F2, if the load of hydraulic actuator 10 further increases and makes Engine torque T rise to Maximum Torque line R, perhaps rise to maximum rated power point K1, in that engine speed and Engine torque mate afterwards on Maximum Torque line R from high speed control zone F1.

Owing to can pass like this, therefore, under the situation before transferring to high speed control zone F1, Working mechanism can with the same peak output that obtains in the past.

That is, transferring under the situation of high speed control zone F1, carrying out along the fine dotted line of Fig. 3 and the control of rising towards Maximum Torque line R from high speed control zone F2.In addition, the control that single-point line expression is directly risen towards Maximum Torque line R from high speed control zone Fn, wherein high speed control zone Fn is positioned at from high speed control zone F2 and transfers to high speed control zone F1 midway.The situation that the state representation of representing with the arrow of thick dashed line is controlled under the state of the high speed control zone F1 that begins before to carry out.In addition, because target engine speed N is according to detected pump capacity D or detected Engine torque T change, therefore, also change of high speed control zone Fn.

Additive method as determining the second desired location B has following method.Promptly, when the pressure reduction of pressing from the load of the output pressure of oil hydraulic pump 6 and hydraulic actuator 10 is lower than under the situation of load sensing pressure reduction, then be judged as output flow deficiency from oil hydraulic pump 6, the pressure reduction of pressing when the output pressure of oil hydraulic pump 6 and the load of hydraulic actuator 10 is defined as the second desired location B with the position of this moment when the state consistent with load sensing pressure reduction begins to be tending towards reducing.

At this moment, on the F2 of high speed control zone, be in the state of POF deficiency, in other words, can be judged as the state that oil hydraulic pump 6 reaches the second regulation pump capacity D.Therefore, carry out high speed control zone F2 is transferred to the control of high speed rotating area side, so that motor can rotate in the high speed rotating zone.

In the above-described embodiments, be that example is illustrated as oil hydraulic circuit with oil hydraulic circuit with load sensing controlled device.But, in the method for the pump capacity of obtaining oil hydraulic pump 6 from the moment of torsion line chart of the measured value of engine speed and motor or utilize pump swash plate angle transducer directly to obtain the method for pump capacity, even oil hydraulic circuit as shown in figure 11 constitutes neutral fully opened type (a just プ Application セ Application タタイプ), also can obtain pump capacity equally.

As the oil hydraulic circuit that adopts at building machineries such as hydraulic shovels, known have a neutral fully opened type oil hydraulic circuit.An example as this oil hydraulic circuit has oil hydraulic circuit as shown in figure 11.In Figure 11, the device of representing with reference character 8 is known pump capacity control device, and its detailed structure for example is disclosed in (Japan) special fair 6-58111 communique.The roughly situation of the apparatus for controlling pump 8 among Figure 11 is described below: be arranged on the centre by-pass loop of control valve 9 throttle valve ( り) 30 upstream pressure imports to the apparatus for controlling pump 8 of variable capacity type oil hydraulic pump 6 by guide's oil circuit 28.

So, when control valve 9 from the neutral position (II) towards (I) position or (III) during the locality operation, then the flow in the centre by-pass loop by control valve 9 reduces gradually, the pressure of the upstream side of throttle valve 30 also reduces gradually.The pump capacity of variable capacity type oil hydraulic pump 6 increases with the form that the upstream side pressure with throttle valve 30 is inversely proportional to.When control valve 9 switches to (I) position or (III) during the position, because the centre by-pass loop is blocked, therefore, the upstream side pressure of throttle valve 30 reaches the pressure with fuel tank 22 pars fully.

At this moment, variable capacity type oil hydraulic pump 6 reaches maximum pump capacity.So, reached the pressure of fuel tank 22 by the pressure that detects guide's oil circuit 28, can control engine speed.

Perhaps, also can use the method for the pump capacity of obtaining variable capacity type oil hydraulic pump 6 from the measured value and the Engine torque of engine speed or utilize pump swash plate angle transducer directly to obtain the method for pump capacity, the control engine speed.

Therefore, oil hydraulic circuit of the present invention is not limited to the oil hydraulic circuit of load sensing type.

When the load of hydraulic actuator 10 when the state that increases reduces gradually, then controller 7 makes this load and Engine torque mate on Maximum Torque line R and makes this load minimizing.If obtain the relation that target engine speed N and detected pump capacity D change accordingly, then, make for example high speed control zone Fn decline from the Maximum Torque line R of this moment and the match point of high speed control zone F3 from Fig. 7.

In addition, at target engine speed N after the second target engine speed N2 transfers to the first target engine speed N1, even the high speed control zone makes Engine torque T drop to maximum rated power point K1 when high speed control zone F1 shifts.

Then, as operating stem 11a during from the recovering state operated significantly, then the swash plate angle of oil hydraulic pump 6 diminishes, and controller 7 control fuel injection systems 3 reduce fuel injection amount.Like this, in high speed control zone Fn or high speed control zone F1, make engine load and Engine torque coupling, simultaneously, make of the control of the pump capacity of oil hydraulic pump 6 from maximum pump capacity state minimizing.

When in the F1 of high speed control zone, making engine load and Engine torque coupling and reducing the control of Engine torque T simultaneously, the pump capacity of oil hydraulic pump 6 reduces than the first regulation pump capacity D1, when the pump capacity D of oil hydraulic pump 6 tended to further reduce, the drive controlling of carrying out motor was to reach the target engine speed N corresponding to detected pump capacity D that obtains from Fig. 7.

Point on the high speed control zone F1 of this moment can be used as the first desired location A (that is the first regulation pump capacity D1) and sets.The first regulation pump capacity D1 can be used as the maximum pump capacity of oil hydraulic pump 6 and sets, and also can be used as the following value of maximum pump capacity and sets.

The pump capacity of oil hydraulic pump 6 reduces than the first regulation pump capacity D1 and the position of the pump capacity of oil hydraulic pump 6 when tending to reduce is set to the first desired location A, in addition, and also can the following setting first desired location A.That is the point on the high speed control zone F1 when, the pressure reduction of the load of the output pressure of oil hydraulic pump 6 and hydraulic actuator 10 pressure surpasses the load sensing pressure reduction of being set by apparatus for controlling pump 8 can be set to the first desired location A.

Like this, can make the control of engine load and Engine torque coupling.Therefore, can make motor 2, can seek to reduce the fuel consumption of motor 2 in the rotation of low speed rotation area side.

The situation that expression is shifted to high speed control zone Fn from high speed control zone F1 in Fig. 4.In addition, set the pump capacity value of judging the first desired location A for identical value with the pump capacity value of judging the second desired location B, also can set different value for.

And, can press the variance ratio of P, the position of changing the first desired location A according to the output of the variance ratio of the pump capacity of the variance ratio of Engine torque T, oil hydraulic pump 6 or oil hydraulic pump 6.That is, when the degree that promptly reduces when these variance ratio was high, the position of the first desired location A was set at the high position side of Engine torque, can shift to high speed control zone F2 ahead of time.

According to the present invention, can reduce the fuel consumption of motor, and the first target engine speed N1 setting high-speed control area F 1 according to the command value setting in the corresponding fuel dial 4 of operator, preestablish the second target engine speed N2 and the high speed control zone F2 of low speed rotation area side according to the first target engine speed N1 that sets, high speed control zone F1, based on the second target engine speed N2 or high speed control zone F2, the drive controlling of beginning motor.

Thus, in the zone that does not need high Engine torque, can control the rotating speed of motor, thereby can reduce the fuel consumption of motor based on the second target engine speed N2 of low speed rotation area side.In addition, in the zone of the high Engine torque of needs, the drive controlling that can carry out motor to be reaching the predefined target engine speed N according to detected pump capacity D, and can fully obtain the required operating speed of operation task mechanism.

In addition, when the high output state from motor reduced Engine torque T, the drive controlling that also can carry out motor to be reaching the predefined target engine speed N according to detected pump capacity D, thereby can seek to reduce fuel consumption.

Also can be suitable for situation of the present invention well even more than utilize Figure 11 to illustrate in neutral fully opened type oil hydraulic circuit, as neutral fully opened type oil hydraulic circuit, known have minus flow control type oil hydraulic circuit and a positive flow control type oil hydraulic circuit.At this, narrate the embodiment in minus flow control type oil hydraulic circuit and the positive flow control type oil hydraulic circuit in further detail.

Below, utilize Figure 12 that the embodiment who adopts minus flow control type oil hydraulic circuit is described.In addition, utilize Figure 13 that the control characteristic of the minus flow control valve 59 in minus flow control type oil hydraulic circuit shown in Figure 12 is described, and utilize Figure 14 that pump control characteristic in minus flow control type oil hydraulic circuit shown in Figure 12 is described.

As shown in figure 12, in minus flow control type oil hydraulic circuit, by not shown motor variable capacity type oil hydraulic pump 50 is driven and rotate, the output flow of exporting from variable capacity type oil hydraulic pump 50 is fed into first control valve 51, second control valve 52 and the 3rd control valve 53.The 3rd control valve 53 constitutes the operating valve of operation hydraulic actuator 60, though omitted record about the reference character of hydraulic actuator,, first control valve 51 and second control valve 52 constitute the operating valve of operation hydraulic actuator respectively.

In addition, the pilot valve of operating first control valve 51～the 3rd control valve 53 in Figure 12 respectively can constitute as shown in Figure 15, and expression positive flow control type oil hydraulic circuit described later has omitted pilot valve in Figure 12 in this Figure 15.

The centre by-pass loop 54a of first control valve 51 is connected with the centre by-pass loop 54b of second control valve 52, and the centre by-pass loop 54b of second control valve 52 is connected with the centre by-pass loop 54c of the 3rd control valve 53.The centre by-pass loop 54c of the 3rd control valve 53 is connected with centre by-pass loop 54, and this centre by-pass loop 54 is communicated with fuel tank 22, is provided with throttle valve 55 in centre by-pass loop 54.

The pressure P t of the upstream side of throttle valve 55 is discharged by oil circuit 63, and the pressure P d in the downstream side of throttle valve 55 is discharged by oil circuit 64.The front and back pressure reduction (Pt-Pd) of throttle valve 55 is that the pressure difference between oil circuit 63 and the oil circuit 64 can be detected by pressure transducer 62.

The driving that guide's oil hydraulic pump 56 constitutes by not shown motor is driven in rotation.Output flow from guide's oil hydraulic pump 56 supplies to minus flow control valve 59 and servo pilot valve 58.In addition, the output pressure from guide's oil hydraulic pump 56 is not adjusted into and can rises to more than the authorized pressure by pressure by relief valve 67.

The swash plate angle of the swash plate 50a of the pump capacity of control variable capacity type oil hydraulic pump 50 is by servo-hydraulic actuator 57,

servo pilot valve

58 and 59 controls of minus flow control valve.Minus flow control valve 59 constitutes the switching valve of two-bit triplet, at a distolateral pressure P d that the spring force and the downstream side of the throttle valve 55 that is arranged on centre by-pass loop 54 are arranged by oil circuit 64 effects of minus flow control valve 59.

In addition, distolateral at another of minus flow control valve 59, by oil circuit 63 effects the pressure P t of the upstream side of throttle valve 55 is arranged, effect has from the output of minus flow control valve 59 and presses Pn in addition.Output presses Pn the output from guide's oil hydraulic pump 56 that supplies to via oil circuit 65 to be pressed as initial press and pressed by the output of minus flow control valve 59 controls, can be detected by pressure transducer 61.

Minus flow control valve 59 utilizes spring force to be switched to the position from the output flow of guide's oil hydraulic pump 56 that output is supplied with via oil circuit 65 usually, but, if it is big that the front and back pressure reduction (Pt-Pd) of throttle valve 55 becomes, then be switched to the position that makes from the output flow minimizing of minus flow control valve 59.

That is, minus flow control valve 59 is controlled according to the front and back pressure reduction (Pt-Pd) of throttle valve 55.When front and back pressure reduction (Pt-Pd) becomes big, make the control that reduces from the output flow of minus flow control valve 59, when front and back pressure reduction (Pt-Pd) when diminishing, the control that the output flow from minus flow control valve 59 is increased.

Servo pilot valve 58 constitutes the switching valve of 3-position 4-way, presses Pn to act on the distolateral of servo guiding valve from the output of minus flow control valve 59 output, and it is distolateral that spring force acts on another of servo guiding valve.In addition, be supplied to from the output flow of guide's oil hydraulic pump 56 servo action portion via servo pilot valve 58.In addition, the servo action portion of servo pilot valve 58 is connected via the servopiston 57a of linkage part 66 with the servo-hydraulic actuator 57 of the swash plate 50a rotation that makes variable capacity type oil hydraulic pump 50.

The hydraulic chamber of the port of servo pilot valve 58 and servo-hydraulic actuator 57 is connected via the servo action portion of servo pilot valve 58.In addition, the servopiston 57a of servo-hydraulic actuator 57 active force that utilizes spring applies power towards minimum swash plate direction to swash plate 50a.

The action of the pump capacity of control variable capacity type oil hydraulic pump 50 then, is described.For example, (II) operates (I) position or (III) position from the neutral position by being operated by not shown pilot valve when the 3rd control valve 53, and then the centre by-pass loop 54c of the 3rd control valve 53 is gradually by throttling.Simultaneously, the loop that is connected with hydraulic actuator 60 is opened gradually, can make hydraulic actuator 60 actions.Along with centre by-pass loop 54c gradually by throttling, the flow that flows through centre by-pass loop 54 reduces, thus the front and back pressure reduction (Pt-Pd) of throttle valve 55 reduces.

When the front and back of throttle valve 55 pressure reduction (Pt-Pd) reduced, then effect had the minus flow control valve 59 of the front and back pressure reduction (Pt-Pd) of throttle valve 55 to be switched to the switching position on the right side of Figure 12 because of the active force of spring.That is, as shown in figure 13,, press Pn to rise from the output of minus flow control valve 59 outputs along with front and back pressure reduction (Pt-Pd) minimizing of throttle valve 55.

Transverse axis is represented the front and back pressure reduction (Pt-Pd) of throttle valve 55 in Figure 13, and the longitudinal axis is represented to press Pn from the output of minus flow control valve 59 outputs.

Press Pn when output and rise, the guiding valve of servo pilot valve 58 to slip, makes servo pilot valve 58 switch to the switching position on right side among Figure 12 to the left of Figure 12.Then, supply to the output flow from guide's oil hydraulic pump 56 of servo pilot valve 58, be directed to the right side hydraulic chamber of servo-hydraulic actuator 57 from servo pilot valve 58.

Thus, the servopiston 57a of servo-hydraulic actuator 57 overcome spring force to the left of Figure 12 to slip, so that the mode that the pump capacity of variable capacity type oil hydraulic pump 50 increases is rotated swash plate 50a.In addition, the swash plate angle in the variable capacity type oil hydraulic pump 50 is controlled, made the required flow of hydraulic actuator 60 actions so that reach from the output flow of variable capacity type oil hydraulic pump 50 output.

By servopiston 57a towards the left of Figure 12 to slip, the servo action portion of servo pilot valve 58 via linkage part 66 towards the left of Figure 12 to slip, make servo pilot valve 58 get back to the neutral position.

In addition, when pressing Pn to reach to press corresponding to the output of the front and back pressure reduction (Pt-Pd) of throttle valve 55 from the output of minus flow control valve 59, servo pilot valve 58 obtains balance and maintains the neutral position.At this moment, the sliding position of the servopiston 57a of servo-hydraulic actuator 57 becomes the position of pressing Pn corresponding to output, as shown in figure 14, as the pump capacity D of variable capacity type oil hydraulic pump 50 can reach press Pn corresponding to output pump capacity D promptly, corresponding to the pump capacity D of the front and back pressure reduction (Pt-Pd) of throttle valve 55.

In Figure 14, transverse axis is represented to press joint Pn from the output of minus flow control valve 59 outputs, and the longitudinal axis is represented the pump capacity D of variable capacity type oil hydraulic pump 50.

As previously mentioned, in the explanation of using neutral fully opened type oil hydraulic circuit shown in Figure 15 to carry out, as the method for the pump capacity of obtaining oil hydraulic pump, illustrated that the method obtained from the moment of torsion line chart of the measured value of engine speed and motor, the swash plate angle transducer that utilizes oil hydraulic pump directly obtain the method for pump capacity.Although understand by detecting pressure in guide's oil circuit 28 and reached tank pressure and come control that engine speed is carried out, but, in minus flow control type oil hydraulic circuit as shown in figure 12, and then Pn is pressed in detection from the output of minus flow control valve 59 output pressure transducer 61 is set, and utilize the performance plot of Figure 14, also can know the command value D of the pump capacity of indication variable capacity type oil hydraulic pump.

In addition, by the pressure transducer 62 of the front and back pressure reduction (Pt-Pd) that detects throttle valve 55 is set, and utilize the performance plot of Figure 13 and Figure 14, also can know the command value D of the pump capacity of indication variable capacity type oil hydraulic pump 50.

Thereby, even in minus flow control type oil hydraulic circuit, also know the command value D of the pump capacity of indication variable capacity type oil hydraulic pump 50, therefore, can control engine speed.In addition, be updated to controller shown in Figure 17, can control the rotating speed of motor by the value that will obtain like this.

In addition, the speed setting of not shown motor that will drive variable capacity type oil hydraulic pump 50 in Figure 12 is when low speed side, and the centre by-pass flow of the throttle valve 55 by centre by-pass loop 54 reduces.Thus, the front and back pressure reduction (Pt-Pd) of throttle valve 55 diminishes, and as shown in figure 13, presses Pn to increase from the output of minus flow control valve 59 outputs.In addition, based on the performance plot of Figure 14, the pump capacity D of variable capacity type oil hydraulic pump 50 increases.

Like this, even engine speed is set in low speed side, low speed side situation in addition is identical with engine speed is set in, and also can carry out the control of pump capacity D.This just means identical with the situation of load sensing type oil hydraulic circuit, even engine speed is set in low speed side, low speed side situation in addition is same with engine speed is set in, and also can carry out the control of pump capacity D.

Then, use Figure 15 that the embodiment who adopts positive flow control type oil hydraulic circuit is described.About the pump control characteristic in the positive flow control type oil hydraulic circuit shown in Figure 15, use Figure 16 to describe.In addition, in positive flow control type oil hydraulic circuit, adopt the reference character that in Figure 12, uses, thereby omit explanation for same parts for the constituting component identical with minus flow control type oil hydraulic circuit shown in Figure 12.

As shown in figure 15, in positive flow control type oil hydraulic circuit, figure is shown with first pilot valve 71, second pilot valve 72 and the 3rd pilot valve 73 of operating first control valve 51, second control valve 52 and the 3rd control valve 53 respectively.By operating first pilot valve 71～the 3rd pilot valve 73 respectively, make pressure oil output from guide's oil hydraulic pump 56 via the pipe arrangement that dots, can act on each guiding valve of first control valve 51～the 3rd control valve 53.

In addition, according to each operation amount and the direction of operating of first pilot valve 71～the 3rd pilot valve 73, can control corresponding first control valve 51～the 3rd control valve 53 respectively.

Each operation amount of first pilot valve 71～the 3rd pilot valve 73 can be detected by pressure transducer 74a～74f, and this pressure transducer 74a～74f is separately positioned on each pipe arrangement that dots that connects first pilot valve 71～the 3rd pilot valve 73 and first control valve 51～the 3rd control valve 53.

Be imported into controller 75 by the detected detected pressures of each pressure transducer 74a～74f via the electric wiring of representing with a～f.When to first control valve 51～when the 3rd control valve 53 carried out a plurality of operation, detected detected pressures from pressure transducer 74a～74f was imported into controller 75 respectively.The computing of the value of closing of a plurality of detected pressures that in controller 75, are input to, thus from the value of closing of the detected pressures of the transverse axis that is illustrated in Figure 16, determine command value D corresponding to the pump capacity of this value of closing.

Then, the command value D of the pump capacity that is determined outputs to apparatus for controlling pump 76 and control pump control gear 76, so that the pump capacity of variable capacity type oil hydraulic pump 50 reaches command value D.For example, when first pilot valve 71 and second pilot valve 72 are operated, by first control valve 51 and second control valve 52, supply to not shown hydraulic actuator from the output flow of variable capacity type oil hydraulic pump 50.

In the case of the above embodiments, if first pilot valve 71 and second pilot valve 72 are not operated to total travel, then first control valve 51 and second control valve of being operated by first pilot valve 71 and second pilot valve 72 respectively 52 is not switched to the total travel position yet, therefore, Sheng Xia oil is back to fuel tank 22 by centre by-pass loop 54.

Therefore, even in so positive flow control type oil hydraulic circuit,, can carry out respectively speed controlling by each hydraulic actuator of first pilot valve 71～the 3rd pilot valve 73 operations by operating first pilot valve 71～the 3rd pilot valve 73 respectively.

And therefore the command value D owing to determined the pump capacity in the above-mentioned positive flow control type oil hydraulic circuits by controller 75, by using the command value D of the pump capacity of being determined by controller 75, can control engine speed.

Therefore, oil hydraulic circuit of the present invention is not limited to load sensing type oil hydraulic circuit, even neutral fully opened type oil hydraulic circuit, promptly, even minus flow control type oil hydraulic circuit in the neutral fully opened type oil hydraulic circuit or positive flow control type oil hydraulic circuit also can be suitable for the present invention well.

Industrial applicibility

The present invention can make technological thought of the present invention be applicable to the engine control of Diesel engine.

Claims

1. the control gear of a motor has:

Oil hydraulic pump, it is a variable capacity type, is driven by motor;

Hydraulic actuator, it is used to be driven from the pressure oil output of described oil hydraulic pump;

Control valve, its control make pressure oil supply with or discharge from described hydraulic actuator to described hydraulic actuator from the pressure oil of described oil hydraulic pump output;

Feeler mechanism, it detects the pump capacity and the Engine torque of described oil hydraulic pump; And

Fuel injection system, the fuel that its control is supplied with to described motor,

The control gear of this motor is characterised in that to have:

Command device, it is selected a command value and sends instruction from the command value that can carry out variable instruction;

First setting device, its command value of sending according to described command device is set first target engine speed, and based on described first target engine speed of setting, sets second target engine speed lower than described first target engine speed;

Second setting device, it sets the pump capacity that detected by described feeler mechanism and the corresponding relation between the target engine speed and the Engine torque that detected by described feeler mechanism and the corresponding relation between the target engine speed,

In the drive controlling of the described motor that begins based on described second target engine speed to carry out, corresponding with detected pump capacity of described feeler mechanism or Engine torque and control described fuel injection system, to reach the target engine speed that described second setting device is obtained.

2. the control gear of motor as claimed in claim 1 is characterized in that,

In the control of the motor that carries out based on described second target engine speed, the control of fuel that the target engine speed based on being obtained by described second setting device in the described fuel injection system is carried out be pump capacity at described oil hydraulic pump greater than the predefined second regulation pump capacity after, perhaps after Engine torque is greater than the predefined second regulation Engine torque, carry out.

3. the control gear of motor as claimed in claim 1 or 2 is characterized in that,

In the control of the motor that carries out based on described first target engine speed, the control of fuel that the target engine speed based on being obtained by described second setting device in the described fuel injection system is carried out be pump capacity at described oil hydraulic pump less than the predefined first regulation pump capacity after, perhaps after Engine torque is less than the predefined first regulation Engine torque, carry out.

4. as the control gear of each described motor in the claim 1 to 3, it is characterized in that,

The target engine speed of being obtained by described second setting device is meant, the target engine speed corresponding with described feeler mechanism detected pump capacity and with the corresponding target engine speed of described feeler mechanism detected Engine torque in the target engine speed of higher side.

5. the controlling method of a motor, the control gear of this motor has:

Oil hydraulic pump, it is a variable capacity type, is driven by motor;

Control valve, its control make pressure oil supply with or discharge from described hydraulic actuator to described hydraulic actuator from the pressure oil of described oil hydraulic pump output; And

Feeler mechanism, it detects the pump capacity and the Engine torque of described oil hydraulic pump,

The controlling method of this motor is characterised in that,

From the command value that can carry out variable instruction, select a command value, and set first target engine speed according to the command value of selecting;

Set second target engine speed lower based on described first target engine speed of setting than described first target engine speed;

Preestablish the corresponding target engine speed of Engine torque that the pump capacity that detects with described feeler mechanism or described feeler mechanism are detected;

The drive controlling that begins the described motor that carries out based on described second target engine speed according in predefined described target engine speed, the target engine speed corresponding with detected pump capacity of described feeler mechanism or Engine torque control.

6. the controlling method of motor as claimed in claim 5 is characterized in that,

In the control of the motor that carries out based on described second target engine speed, the drive controlling of the described motor that carries out based on described target engine speed be pump capacity at described oil hydraulic pump greater than the predefined second regulation pump capacity after, perhaps after Engine torque is greater than the predefined second regulation Engine torque, carry out.

7. as the controlling method of claim 5 or 6 described motors, it is characterized in that,

In the control of the motor that carries out based on described first target engine speed, the drive controlling of the described motor that carries out based on described target engine speed be pump capacity at described oil hydraulic pump less than the predefined first regulation pump capacity after, perhaps after Engine torque is less than the predefined first regulation Engine torque, carry out.

8. as the controlling method of each described motor in the claim 5 to 7, it is characterized in that,

The drive controlling of the described motor that carries out based on described target engine speed is controlled according to the target engine speed corresponding with described feeler mechanism detected pump capacity.

9. as the controlling method of each described motor in the claim 5 to 7, it is characterized in that,

The drive controlling of the described motor that carries out based on described target engine speed is to control according to the target engine speed corresponding with described feeler mechanism detected Engine torque.

10. as the controlling method of each described motor in the claim 5 to 7, it is characterized in that,

The drive controlling of the described motor that carries out based on described target engine speed according in predefined target engine speed, the target engine speed corresponding with described feeler mechanism detected pump capacity and with the corresponding target engine speed of described feeler mechanism detected Engine torque in the target engine speed of higher side control.